CN103228954B - Vehicular power transmission device - Google Patents

Vehicular power transmission device Download PDF

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Publication number
CN103228954B
CN103228954B CN201080070340.1A CN201080070340A CN103228954B CN 103228954 B CN103228954 B CN 103228954B CN 201080070340 A CN201080070340 A CN 201080070340A CN 103228954 B CN103228954 B CN 103228954B
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CN
China
Prior art keywords
motor
mentioned
converters
torque
rotary component
Prior art date
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Expired - Fee Related
Application number
CN201080070340.1A
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Chinese (zh)
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CN103228954A (en
Inventor
出盐幸彦
宫崎光史
神谷敏彦
江藤真吾
浅冈博则
加藤康之
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Toyota Motor Corp
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Toyota Motor Corp
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Publication of CN103228954A publication Critical patent/CN103228954A/en
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Publication of CN103228954B publication Critical patent/CN103228954B/en
Expired - Fee Related legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
    • B60W10/023—Fluid clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H41/00—Rotary fluid gearing of the hydrokinetic type
    • F16H41/24—Details
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
    • B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4825—Electric machine connected or connectable to gearbox input shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W2510/00—Input parameters relating to a particular sub-units
    • B60W2510/02—Clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H2045/002—Combinations of fluid gearings for conveying rotary motion with couplings or clutches comprising a clutch between prime mover and fluid gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S903/00—Hybrid electric vehicles, HEVS
    • Y10S903/902—Prime movers comprising electrical and internal combustion motors

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Arrangement Of Transmissions (AREA)
  • General Details Of Gearings (AREA)

Abstract

Provided is a vehicular power transmission device that is provided with a hydraulic power transmission device, and that is able to have a shorter overall length in the axial direction. The vehicular power transmission device is provided with a transaxle case (22) that is divided by a partition (68) provided to the reverse side of a torque converter (18) from an engine (14) and that has: a first chamber (R1) that houses the torque converter (18); and a second chamber (R2) formed on the reverse side of the partition (68) from the torque converter (18). The first chamber (R1) and second chamber (R2) are isolated from each other in an oil-tight fashion by means of an oil seal (70) that, in an oil-tight manner, seals the gap between the inner peripheral surface of a through-hole (69) formed in the partition (68) and the outer peripheral surface of a tube-shaped pump drive shaft (58). A first thrust bearing (94) is disposed between a starter (46) and a side-wall section that is at the partition (68) side of a rear cover (38). The first thrust bearing (94) is provided in a manner so that a portion overlaps with the oil seal (70) in a view from a direction perpendicular to a first shaft center (C1).

Description

Power transmission apparatus for vehicle
Technical field
The present invention relates to the structure of the power transmission apparatus for vehicle of a part for the power transfer path formed between motor and driving wheel.
Background technique
The power transfer path that there will be a known between motor and driving wheel possesses the power transmission apparatus for vehicle of torque-converters, and wherein, this torque-converters possesses: the input side rotary component being provided with multiple pump blade; Be provided with the outlet side rotary component accepted from multiple turbine blades of the fluid stream of this pump blade; And be provided be disposed between said pump blade and turbine blade determine leaf blade determine leaf.Such as, what record in patent documentation 1 to 4 is exactly such power transmission apparatus for vehicle.
Patent documentation 1: Japanese Unexamined Patent Publication 2010-105450 publication
Patent documentation 2: Japanese Unexamined Patent Publication 2008-138877 publication
Patent documentation 3: Korean Patent No KR100755046(B1)
Patent documentation 4: Japanese Unexamined Patent Publication 2007-22112 publication
But, in above-mentioned power transmission apparatus for vehicle in the past, in order to improve the lift-launch towards vehicle, expect the entire axial length shortening this power transmission apparatus for vehicle further.To this, such as consider following method: make the slimming and make it shorten in the axial direction on the axis direction of this torque-converters of the component parts of torque-converters, thus, reduce the distance on above-mentioned axis direction that this torque-converters is shared in power transmission apparatus for vehicle, shorten the entire axial length of power transmission apparatus for vehicle.But there is the limit in the slimming of above-mentioned component parts.In addition, torque-converters one of the main reasons elongated on its axis direction is below enumerated.That is: in the outer cover being incorporated in torque-converters and the overrunning clutch be installed between Ding Ye and such as housing parts etc. needs to have on above-mentioned axis direction the width dimensions of regulation in order to ensure the torque capacity of regulation.
Summary of the invention
The present invention completes for background with above-mentioned situation, its object is to, in the power transmission apparatus for vehicle possessing torque-converters, provides a kind of power transmission apparatus for vehicle that can shorten entire axial length.
Purport of the present invention for reaching above-mentioned purpose is: the power transfer path of (a) power transmission apparatus for vehicle between motor and driving wheel possesses torque-converters, and above-mentioned torque-converters has: the input side rotary component being provided with multiple pump blade; Be provided with the outlet side rotary component accepted from multiple turbine blades of the fluid stream of said pump blade; and be provided be disposed between said pump blade and above-mentioned turbine blade determine leaf blade determine leaf, wherein, b () above-mentioned power transmission apparatus for vehicle possesses housing, above-mentioned housing has by being arranged at the separated with the spacing wall of above-mentioned motor opposition side of above-mentioned torque-converters, receive above-mentioned torque-converters the first Room and be formed at above-mentioned spacing wall with the second Room of above-mentioned torque-converters opposition side, c () above-mentioned first Room and above-mentioned second Room are isolated mutually in liquid-tight manner by oil sealing, above-mentioned oil sealing seal in liquid-tight manner above-mentioned spacing wall inner peripheral surface and from above-mentioned input side rotary component towards the gap between the outer circumferential face of the projecting cylindric running shaft in above-mentioned second side, Room, d () is in the sidewall portion by above-mentioned spacing wall side of above-mentioned input side rotary component and above-mentionedly determine to be equipped with thrust-bearing between leaf, when () above-mentioned thrust-bearing is arranged to observe from the direction orthogonal with the axle center of above-mentioned torque-converters e, part or all is overlapping with above-mentioned oil sealing, f () determines leaf and supports between the above-mentioned on-rotatably moving part determining leaf to be provided with overrunning clutch above-mentioned, a part for above-mentioned overrunning clutch is compared the above-mentioned inner ring determining leaf and above-mentioned overrunning clutch and is given prominence to towards above-mentioned second side, Room, g () above-mentioned input side rotary component has cyclic lug, above-mentioned cyclic lug by above-mentioned input side rotary component by above-mentioned spacing wall side sidewall portion in, a part for the radial position corresponding with above-mentioned thrust-bearing is given prominence to towards above-mentioned spacing wall side throughout complete cycle and is formed, (h) above-mentioned thrust bearing division, a part for above-mentioned overrunning clutch is accommodated in above-mentioned cyclic lug.
So, with above-mentioned thrust-bearing when observing from the direction orthogonal with above-mentioned axle center not compared with the situation of above-mentioned oil sealing overlap, parts such as the overrunning clutch be installed between Ding Ye and such as housing parts etc. that this thrust-bearing and this thrust-bearing can be adjoined arranging configures near spacing wall side, therefore, it is possible to shorten the distance between the outer cover entirety of the torque-converters of the above-mentioned thrust-bearing of storage and overrunning clutch and spacing wall.Therefore, it is possible to shorten the entire axial length of power transmission apparatus for vehicle.
In addition, preferably, above-mentioned torque-converters possesses motor and intermittently uses clutch, above-mentioned motor intermittently optionally links the bent axle of above-mentioned motor and the input side rotary component of above-mentioned torque-converters with clutch, and above-mentioned motor to be intermittently incorporated in above-mentioned input side rotary component by the above-mentioned engine side that clutch is in above-mentioned outlet side rotary component and from part or all state overlapping with above-mentioned oil sealing and above-mentioned thrust-bearing when observing with the direction of above-mentioned axis parallel.According to the present invention, owing to above-mentioned thrust-bearing, overrunning clutch being configured near spacing wall side, above-mentioned motor intermittently can be configured in compactly the space vacated of the engine side in the outer cover of torque-converters thus with clutch.
In addition, preferably, a () above-mentioned power transmission apparatus for vehicle possesses motor, above-mentioned motor is configured on the second axle center with above-mentioned axis parallel, and respectively via above-mentioned cylindric running shaft and be linked to the motor link rotary component of above-mentioned cylindric running shaft and above-mentioned input side rotary component links, b () above-mentioned spacing wall has support, above-mentioned support is given prominence to towards above-mentioned second side, Room throughout complete cycle by a part for the radial position of above-mentioned spacing wall and is formed, c () above-mentioned motor link rotary component supports as rotating via the support of bearing by above-mentioned spacing wall, d () above-mentioned cyclic lug is positioned at the inner circumferential side of the support of above-mentioned spacing wall.So, such as, by utilizing the output of above-mentioned motor to this motor assist or make engine stop and utilize above-mentioned motor car etc. when making vehicle travel by motor, the fuel availability of vehicle can be improved.In addition, even if when arranging motor link rotary component respectively to be linked by the input side rotary component of motor and torque-converters and being used for this motor link rotary component to support the support of the spacing wall for rotating, also above-mentioned thrust-bearing, above-mentioned overrunning clutch can be configured near spacing wall side.
In addition, preferably, a () above-mentioned power transmission apparatus for vehicle possesses driving mechanism, above-mentioned driving mechanism is configured in above-mentioned motor opposition side relative to above-mentioned torque-converters on above-mentioned axis direction, and the power from above-mentioned torque-converters is transmitted towards above-mentioned driving wheel, b () above-mentioned outlet side rotary component is linking by the position of above-mentioned driving mechanism side and the input shaft of above-mentioned driving mechanism relative to said pump blade on above-mentioned axis direction, c () above-mentioned determine leaf via overrunning clutch with determine rachis and link in the mode that can not relatively rotate, the inner ring of (d) above-mentioned overrunning clutch with above-mentioned determine linking portion that rachis links and above-mentioned outlet side rotary component be arranged to observe from the direction orthogonal with above-mentioned axle center with the linking portion that above-mentioned input shaft links time part or all is overlapping with above-mentioned thrust-bearing and above-mentioned oil sealing respectively.So, the linking portion linked with input shaft of outlet side rotary component and the inner ring of overrunning clutch with determine the linking portion that rachis links and be arranged on outside the outer cover of torque-converters on above-mentioned axis direction.Therefore, compared with being arranged on the situation in above-mentioned outer cover with above-mentioned each linking portion, the length on axis direction of this outer cover can be shortened, therefore, it is possible to shorten the entire axial length of power transmission apparatus for vehicle.
Accompanying drawing explanation
Fig. 1 illustrates in the vehicle of the power transmission apparatus for vehicle possessing one embodiment of the invention, from the motor of the actuating force source as this vehicle via the figure of power transmitting deice to the power transfer path of driving wheel.
Fig. 2 is the sectional view of the major component of the power transmitting deice that Fig. 1 is shown.
Fig. 3 is the figure observed from arrow III direction amplifying the part of being surrounded by dot and dash line illustrated in Fig. 2.
Fig. 4 is the sectional view from the cross section that the direction of arrow is observed of the IV-IV line illustrated along Fig. 3.
Fig. 5 is the sectional view from the cross section that the direction of arrow is observed of the V-V line illustrated along Fig. 3.
Embodiment
Below, with reference to accompanying drawing, one embodiment of the invention are described in detail.In addition, below in an example accompanying drawing suitably simplified or be out of shape, the size ratio and shape etc. in each portion may not be described exactly.
Embodiment 1
Fig. 1 illustrates possessing the power transmission apparatus for vehicle 12(of one embodiment of the invention hereinafter referred to as " power transmitting deice 12 ") vehicle 10 in, from the motor 14 of the actuating force source as this vehicle 10 via the figure of power transmitting deice 12 to the power transfer path of driving wheel 16.Fig. 2 illustrates major component, the i.e. torque-converters 18 of above-mentioned power transmitting deice 12, the sectional view of automatic transmission 20 and motor MG etc.First axle center C1 is the axle center of torque-converters 18 and automatic transmission 20 etc.In addition, eliminate in fig. 2 than the first axle center C1 lower half portion on the lower.
As shown in Figure 1, power transmitting deice 12 has the driving axle housing (housing) 22 being such as installed on vehicle body by screw threads for fastening etc., possessing the power transfer path that is arranged between motor 14 and driving wheel 16 in this driving axle housing 22 and connect successively from motor 14 side on the first axle center C1 torque-converters 18, oil pump 24 and the automatic transmission 20 that arrange.In addition, power transmitting deice 12 possesses motor MG, and this motor MG is disposed on the second axle center C2 parallel with the first axle center C1, and with the input side rotary component (back cover 38 described later) of torque-converters 18 can the mode of transferring power link.In addition, above-mentioned second axle center C2 is equivalent to the second axle center with the axis parallel of torque-converters 18.
In addition, power transmitting deice 12 possesses in driving axle housing 22: be arranged at the running shaft parallel with the first axle center C1 integratedly, and the counter driven gear 28 engaged with output block that is the output gear 26 of automatic transmission 20; Be arranged at final-stage gear between the running shaft parallel with above-mentioned first axle center C1 and a pair axletree 30 to 32; And by from this final-stage gear to 32 the power of driven gear respectively towards the differential gearing 34 that a pair axletree 30 transmits.
The power transmitting deice 12 of such formation is horizontally placed on such as front wheel driving ejector half and FF(front-mounted engine/front-wheel drive together with motor 14) front of the vehicle 10 of type.Further, vehicle 10 is driven by least one party in motor 14 and motor MG.When the driving of this vehicle 10, from motor 14 and motor MG power successively via torque-converters 18, automatic transmission 20, counter driven gear 28, final-stage gear to 32, differential gearing 34 and a pair axletree 30 transmit respectively towards pair of driving wheels 16.
Below, Fig. 2 to Fig. 5 is used to be described in detail to each device that power transmitting deice 12 possesses.
Automatic transmission 20 is well-known multiple-speed gear-boxes, the first C1 direction, axle center is configured at and motor 14 opposition side relative to torque-converters 18, is equivalent to the driving mechanism of the present invention transmitted towards back segment by the power inputted from torque-converters 18.
Torque-converters 18 is fluid transmission means of a part for the power transfer path formed between motor 14 and driving wheel 16.As shown in Figure 2, torque-converters 18 possesses and to set gradually from above-mentioned motor 14 side on the first axle center C1 and be combined with each other integral and be arranged respectively to the front shroud 36 that can rotate around the first axle center C1 and back cover 38.Front shroud 36 is parts of the bottomed cylindrical towards automatic transmission 20 side opening, and back cover 38 is that peripheral end is towards motor 14 side and front shroud 36 lateral bend and by the discoideus parts of the open end that to be such as fixedly welded on front shroud 36.
Above-mentioned front shroud 36 and back cover 38 play function as input side rotary component, and the power from motor 14 intermittently inputs to this input side rotary component with clutch K0 via motor, thus this input side rotary component rotates.Further, the multiple pump blades 40 arranged in the circumferential direction are fixedly installed in the inner side of back cover 38.
In addition, torque-converters 18 possesses: possess the turbine 42 accepted from multiple turbine blades 44 of the fluid stream of pump blade 40, above-mentioned multiple turbine blade 44 is arranged at the peripheral part of the plectane portion 42c be combined with the peripheral part of lip part 42b by rivet in the circumferential direction with the state that back cover 38 side at pump blade 40 is opposed with this pump blade 40; And determine leaf 46, this is determined leaf 46 and is provided with to be disposed in and determines leaf blade 45 between pump blade 40 and turbine blade 44.Above-mentioned turbine 42 plays function as the outlet side rotary component of torque-converters 18, to be fitted together to link in the mode that can not relatively rotate with the outer circumferential face of the input shaft 48 of automatic transmission 20 by spline.
Front shroud 36 and back cover 38 have receive respectively pump blade 40, turbine blade 44, turbine 42, determine leaf blade 45, determine leaf 46 and the fluid that flows from pump blade 40 towards turbine blade 44, as the function of the outer cover of torque-converters 18.
Fig. 3 amplifies the figure that the part of being surrounded by dot and dash line in Fig. 2 is observed from arrow III direction is shown.As shown in Figure 3, between torque-converters 18 and automatic transmission 20, be equipped with the oil pump 24 of well-known inscribed gear type.This oil pump 24 possesses: the pump cover 50 as on-rotatably moving part being fixed on driving axle housing 22; Be disposed in the position of covering 38 sides rearward of this pump cover 50 and be fixed on the pump housing 52 of this pump cover 50 integratedly; Engage each other and can be incorporated in rotatably inscribed gear in the pump chamber that formed by said pump cover 50 and the pump housing 52 to that is actuation gear 54 and driven gear 56.
The oil pump 24 of such formation by projecting towards automatic transmission 20 side from back cover 38, concentric and diameter is greater than tubular pump live axle 58 rotary actuation of the diameter of this input shaft 48 with input shaft 48.In addition, above described tubular pump live axle 58 is inserted into and is formed in the through hole 60 of the pump housing 52, and links in the mode that can not relatively rotate with actuation gear 54.
In the inner circumferential side of pump cover 50, be fixed with concentric with input shaft 48, that diameter is greater than this input shaft 48 diameter in the mode that can not relatively rotate relative to this pump cover 50 and be less than the on-rotatably moving part of the diameter of tubular pump live axle 58 that is tubulose determine rachis 62.
The leaf 46 of determining of torque-converters 18 links via overrunning clutch 64 and from the tubulose connection shaft 64b that the Inner peripheral portions of the discoideus inner ring 64a of this overrunning clutch 64 is projecting towards the first C1 direction, axle center with the rachis 62 of determining as on-rotatably moving part.Above described tubular connection shaft 64b is that diameter is greater than input shaft 48 and determines the diameter of rachis 62 and be less than the cylinder-like part of the diameter of tubular pump live axle 58.Overrunning clutch 64 possesses the voussoir 64c of size of regulation in large the first C1 direction, axle center of wall thickness had than determining leaf 46, inner ring 64a, to have for stoping when torque-converters 18 carries out determining when moment of torsion amplifies the sufficient torque capacity of leaf 46 counterrotating.Therefore, overrunning clutch 64 is arranged to compare that to determine leaf 46 and inner ring 64a outstanding towards automatic transmission 18 side.
From the front end of the projecting tubulose connection shaft 64b of the Inner peripheral portions of above-mentioned inner ring 64a as used as shown in arrow A in figure 3, compared with on the direction orthogonal with the first axle center C1 pump blade 40 by automatic transmission 20 side position, namely link in the mode that can not relatively rotate by spline is chimeric with the end of determining rachis 62 the outer cover of torque-converters 18 is outer.
In addition, tubulose connection shaft 64b with determine the linking portion (spline telescoping part) that rachis 62 links and be arranged to, when observing from the direction orthogonal with the first axle center C1, a part is overlapping with the pump housing 52 of oil pump 24.The pump housing 52 of above-mentioned oil pump 24 be disposed on the first C1 direction, axle center compare pump blade 40 by automatic transmission 20 side position, namely compare the parts of outer cover by the position of automatic transmission 20 side of torque-converters 18.
Rachis 62 is determined via sleeve (bearing part) 66 supporting for rotating by this in the inner circumferential side that input shaft 48 is determining rachis 62 of automatic transmission 20.
The turbine 42 of torque-converters 18 has: to be fitted together to the boss part 42a of the cylindrical shape linked in the mode that can not relatively rotate by spline with the peripheral part of the input shaft 48 of automatic transmission 20; In the position by motor 14 side of the inner ring 64a of overrunning clutch 64 from a part for the outer circumferential face of above-mentioned boss part 42a towards the projecting lip part 42b of radial outside; And be fixed by caulking to the plectane portion 42c of peripheral part of this lip part 42b.As used shown in arrow B in figure 3, the compare pump blade 40 of above-mentioned boss part 42a on the first C1 direction, axle center leaning on the position of automatic transmission 20 side, namely comparing the position of the outer cover of torque-converters 18 by automatic transmission 20 side, by linking relative to the not revolvable chimeric mode of input shaft 48 and input shaft 48.
In addition, the position of comparing mounted pump blade 40 in back cover 38 of the boss part 42a of turbine 42 on the first C1 direction, axle center leans on the position of automatic transmission 20 side and input shaft 48 to link.
In addition, determine rachis 62 part and position overlapping with the linking portion that input shaft 48 links of turbine 42 when observing from the first C1 direction, axle center, by linking relative to the not revolvable chimeric mode of tubulose connection shaft 64b of overrunning clutch 64 and the tubulose connection shaft 64b of overrunning clutch 64.
In addition, turbine 42 be arranged to observe from the direction orthogonal with the first axle center C1 with the linking portion that input shaft 48 links time a part overlapping with the pump housing 52 of oil pump 24.
And, sleeve 66 is arranged to: on the first C1 direction, axle center the coupling position linked with input shaft 48 comparing turbine 42 by automatic transmission 20 side position, namely compared with the outer cover of torque-converters 18 by the position of automatic transmission 20 side, a part of pump housing 52 with oil pump 24 when observing from the direction orthogonal with the first axle center C1, actuation gear 54 are overlapping.
Driving axle housing 22 has the first Room R1 of storage torque-converters 18 grade and the second Room R2 of storage automatic transmission 20, motor MG and oil pump 24 etc.Above-mentioned first Room R1 and the second Room R2 is separated by the spacing wall 68 be arranged between the back cover 38 of torque-converters 18 and the pump housing 52 of oil pump 24 at the outer circumferential side of tubular pump live axle 58, and mutually sealed in liquid-tight manner by oil sealing 70, this oil sealing 70 seals in liquid-tight manner and is formed at above-mentioned spacing wall 68 and gap between the inner peripheral surface of the through hole 69 inserted for tubular pump live axle 58 and the outer circumferential face of this tubular pump live axle 58.
The side of covering 38 sides rearward of the pump housing 52 along with trend radial outside towards pump cover 50 side namely towards the side away from back cover 38 be taper tilt.Further, the inner peripheral portion 68a of spacing wall 68 is identical with the side of this pump housing 52 is towards the lopsidedness away from back cover 38 towards the pump housing 52 side along with tending to radial outside.
Above-mentioned spacing wall 68 and oil sealing 70 are disposed in compare namely pump blade 40 compares torque-converters 18 parts of outer cover by the position of automatic transmission 20 side by the position of automatic transmission 20 side on the first C1 direction, axle center.Turbine 42 be arranged to observe from the direction orthogonal with the first axle center C1 with the linking portion that input shaft 48 links time a part overlapping with above-mentioned oil sealing 70 and spacing wall 68.
Motor MG is the so-called motor generator set with electric motors function and electricity generate function.As shown in Figure 2, motor MG possesses: the motor stator 72 being fixed on the internal face of driving axle housing 22 by such as bolt; The motor output shaft 74 of the inner circumferential side of above-mentioned motor stator 72 is arranged in the mode that can rotate around the second axle center C2 parallel with the first axle center C1; And the motor rotor 76 of peripheral part of motor output shaft 74 is fixedly installed in the inner circumferential side of motor stator 72.
Above-mentioned motor output shaft 74 is fitted together to by such as spline and is linked to transmission of power running shaft 80 in the mode that can not relatively rotate, and this transmission of power running shaft 80 is supported as rotating around the second axle center C2 by driving axle housing 22 via a pair clutch shaft bearing 78.And, transmission of power running shaft 80 via the Transmitted chains 88 of ring-type so that the mode of transferring power motor link rotary component 84 can be linked to, this Transmitted chains 88 is wrapping with in the first motor link gear 82 and the second motor link gear 86, above-mentioned first motor link gear 82 is arranged at the peripheral part of above-mentioned transmission of power running shaft 80 integratedly, and above-mentioned second motor link gear 86 is arranged on the peripheral part of the motor link rotary component 84 linked with tubular pump live axle 58.Above-mentioned first motor link gear 82 and the second motor link gear 86 be for by the transmission of power from motor MG to the gear of tubular pump live axle 58.Motor MG successively via transmission of power running shaft 80, Transmitted chains 88, motor link rotary component 84, tubular pump live axle 58 active be linked to input side rotary component that is the back cover 38 of torque-converters 18.
As shown in Figure 3, above-mentioned second motor link gear 86 be disposed on the first C1 direction, axle center compare pump blade 40 by automatic transmission 20 side position, namely compare the position of outer cover by automatic transmission 20 side of torque-converters 18.Turbine 42 be arranged to observe from the direction orthogonal with the first axle center C1 with the linking portion that input shaft 48 links time a part overlapping with this second motor link gear 86.
Motor link rotary component 84 possesses: by be formed at spacing wall 68 radial intermediate portion support 68b via the second bearing 90 support into can around first axle center C1 rotate the second motor link gear 86; And link the flange shape connecting member 92 of this second motor link gear 86 and tubular pump live axle 58.The support 68b of above-mentioned spacing wall 68 is given prominence to towards the second R2 side, Room throughout complete cycle by the part being positioned at the radial position of the outer circumferential side of inner peripheral portion 68a in spacing wall 68 and is formed.The inner peripheral surface of the second motor link gear 86 of motor link rotary component 84 supports as rotating via the support 68b of the second bearing 90 by spacing wall 68.
Above-mentioned second bearing 90 and support 68b are disposed in respectively and lean on the position of automatic transmission 20 side relative to pump blade 40, namely compare the position of the outer cover of torque-converters 18 by automatic transmission 20 side on the first C1 direction, axle center.Turbine 42 be arranged to observe from the direction orthogonal with the first axle center C1 with the linking portion that input shaft 48 links time a part overlapping with the support 68b of above-mentioned second bearing 90 and spacing wall 68.
As used shown in arrow C in Fig. 3, the connecting member 92 of motor link rotary component 84 has cylindric boss part 92a, and this boss part 92a to be fitted together to by spline at the inner circumferential side of the through hole 60 of the pump housing 52 and the peripheral part of tubular pump live axle 58 and to link in the mode that can not relatively rotate.In addition, connecting member 92 has lip part 92b, this lip part 92b is projecting towards radial outside from the end by spacing wall 68 side of above-mentioned boss part 92a, identical with the side of the pump housing 52 arranged adjacent on the first C1 direction, axle center, spacing wall 68 is the lopsidedness of court away from back cover 38 towards the pump housing 52 side along with tend to radial outside, and peripheral end links by spline is chimeric with the second motor link gear 86.Turbine 42 be arranged to observe from the direction orthogonal with the first axle center C1 with the linking portion that input shaft 48 links time a part overlapping with the linking portion that tubular pump live axle 58 links (spline embedding part) with connecting member 92.
In the sidewall portion by spacing wall 68 side of back cover 38 with determine to be equipped with the first thrust-bearing 94 between leaf 46, back cover 38 and determine leaf 46 and be arranged to via this first thrust-bearing 94 and can relatively rotate each other.Further, between the lip part 42b determining leaf 46 and turbine 42, clamped the second thrust-bearing 96, determined leaf 46 and turbine 42 and be arranged to via this second thrust-bearing 96 and can relatively rotate each other.
Circular groove 98 is formed in the inner circumferential side of the support 68b of spacing wall 68.Back cover 38 has cyclic lug 38a, namely outstanding towards circular groove 98 side and formed towards the inner peripheral portion 68a side of spacing wall 68 throughout complete cycle by the radial component corresponding with above-mentioned first thrust-bearing 94 in the sidewall portion of spacing wall 68 side by this back cover 38 of this cyclic lug 38a.Cyclic lug 38a is positioned at circular groove 98 in the inner circumferential side of the support 68b of spacing wall 68.Further, above-mentioned first thrust-bearing 94 and be incorporated in the inner side of above-mentioned cyclic lug 38a from a part of determining the overrunning clutch 64 that leaf 46 and inner ring 64a give prominence to.Therefore, overrunning clutch 64 is arranged to compare that to determine leaf 46 and inner ring 64a outstanding towards automatic transmission 18 side.Further, when the first thrust-bearing 94 is arranged to observe from the direction orthogonal with the first axle center C1, a part is overlapping with inner peripheral portion 68a, the support 68b of spacing wall 68 and oil sealing 70 respectively.Further, turbine 42 with the linking portion that input shaft 48 links and tubulose connection shaft 64b with to determine part when linking portion that rachis 62 links is arranged to observe from the direction orthogonal with the first axle center C1 overlapping with the first thrust-bearing 94 and oil sealing 70 respectively.
Motor connection shaft 100 is linked with by such as spline is chimeric at the output shaft of motor 14 that is the output end of bent axle 99.Motor connection shaft 100 is arranged with input shaft 48 is concentric, the front end of the input shaft 48 of automatic transmission 20 with the mode that can relatively rotate embed be formed at this motor connection shaft 100 with in the embedding hole of the cylindric shaft end 100a inner circumferential side of bent axle 99 opposition side, supported as rotating by this cylindric shaft end 100a.
Above-mentioned motor connection shaft 100 has from cylindric shaft end 100a towards the projecting lip part 100b of radial outside.The first vibration damper 102 of the power transfer path be folded between the bent axle 99 of motor 14 and the front shroud 36 of torque-converters 18 is provided with at this lip part 100b.Above-mentioned first vibration damper 102 possesses the damper elastomeric member 103 formed by spring, rubber etc. be installed between inputoutput unit, is to make produce the torsion corresponding to transmitting torque between above-mentioned inputoutput unit thus absorb the damping device impacting, pulse.The pulsation of Engine torque is suppressed by the first vibration damper 102 and transmits towards torque-converters 18.In addition, the first vibration damper 102 is also the vibration damper of the power transfer path be located between above-mentioned motor 14 and above-mentioned motor MG.
Torque-converters 18 possesses the motor optionally linking the bent axle 99 of motor 14 and the front shroud 36 of torque-converters 18 and intermittently uses clutch K0, and this motor is intermittently configured at clutch K0 and compares turbine 42 and lean on the position of motor 14 side and be in the state be incorporated in front shroud 36.
Motor is intermittently wet multi-plate clutch with clutch K0, possesses: link with bent axle 99 via the first vibration damper 102, also plays the clutch hub 104 of function as the output block of the first vibration damper 102; The clutch drum 106 of the cylindrical shape of the front shroud 36 of torque-converters 18 is fixed on integratedly at the outer circumferential side of this clutch hub 104; Time in gap between above-mentioned clutch hub 104 and clutch drum 106 to observe from the direction parallel with the first axle center C1, the mode of overlap configures and a pair first friction plates 108 engaged respectively in the mode that can not relatively rotate with clutch drum 106 respectively; To be configured between above-mentioned a pair first friction plates 108 and the second friction plate 110 engaged in the mode that can not relatively rotate with clutch hub 104; And hydraulic actuator 112, namely this hydraulic actuator 112 pushes in the direction parallel with the first axle center C1 above-mentioned first friction plate 108 and the second friction plate 110 overlapping direction towards them, make above-mentioned first friction plate 108 and the second friction plate 110 mutually friction wedged, thus make clutch hub 104 and clutch drum 106 interconnected.Motor intermittently carries out moment of torsion transmission via the rubbing surface between the opposing party of the rubbing surface between a side of a pair first friction plates 108 and the second friction plate 110 and a pair first friction plates 108 and the second friction plate 110 respectively with clutch K0.In other words, motor intermittently use clutch K0 via two rubbing surfaces by clutch hub 104 and clutch drum 106 interconnected.In addition, motor is intermittently configured in the inner circumferential side of lock-up clutch 120 described later with clutch K0, and when being arranged to observe from the direction orthogonal with the first axle center C1, a part is overlapped with this lock-up clutch 120.
Above-mentioned hydraulic actuator 112 is configured to be had: the piston 112a being disposed in the 36a side, sidewall portion of front shroud 36 relative to the first friction plate 108 and the second friction plate 110; And the pressure chamber 112b formed is surrounded by this piston 112a, front shroud 36 and clutch drum 106.Respectively by the first oil circuit 116, second oil circuit 117 and the 3rd oil circuit 118 supply working oil from hydraulic control circuit 114 towards above-mentioned pressure chamber 112b, wherein, above-mentioned first oil circuit 116 is formed along the first C1 direction, axle center in the input shaft 48 of automatic transmission 20, and with export the hydraulic control circuit 114(of the working oil of hydraulic pressure as former pressure after carrying out pressure regulation produced using oil pump 24 with reference to Fig. 1) be communicated with, above-mentioned second oil circuit 117 is formed at the cylindric shaft end 100a of motor connection shaft 100, and be communicated with above-mentioned first oil circuit 116, above-mentioned 3rd oil circuit 118 is formed at front shroud 36, and be communicated with above-mentioned second oil circuit 117.
Motor intermittently carries out engaging release control with clutch K0 by above-mentioned hydraulic control circuit 114.In above-mentioned engaging release control, by the pressure regulation of the linear solenoid valve in above-mentioned hydraulic control circuit 114 etc., make motor can the torque capacity of transferring power and motor intermittently such as change continuously by the engaging power of clutch K0 intermittently with clutch K0.Intermittently use the fastening state of clutch K0 at motor under, the front shroud 36 as the input side rotary component of torque-converters 18 is rotated integratedly with the bent axle 99 of motor 14.That is, intermittently use the fastening state of clutch K0 at motor under, the front shroud 36 of torque-converters 18 is inputed to via the first vibration damper 102 from the power of motor 14.On the other hand, intermittently use the releasing state of clutch K0 at motor under, the transmission of power between the front shroud 36 of torque-converters 18 and motor 14 is cut off.
Torque-converters 18 possesses the lock-up clutch 120 optionally linking the front shroud 36 as the input side rotary component of this torque-converters 18 and the turbine 42 as outlet side rotary component, this lock-up clutch 120 is configured at compares the position of turbine 42 by motor 14 side, and is in the state be incorporated in front shroud 36.
Lock-up clutch 120 is friction apply clutches, possess: discoideus lock-up clutch piston (piston element) 124, this lock-up clutch piston 124 via second vibration damper 122 that form damping device same with the first vibration damper 102 can the mode of transferring power and the plectane portion 42c of turbine 42 link, and be arranged to can relative to the side wall surface of front shroud 36 close to and leave, as lock-up clutch 120 output block play function; Lock-up clutch friction plate 126, this lock-up clutch friction plate 126 is fixed on the opposed faces opposed with front shroud 36 of this lock-up clutch piston 124; Engaging side grease chamber 128, when lock-up clutch 120 will be made to engage, improves the interior pressure of this engaging side grease chamber 128, is pushed by lock-up clutch piston 124 thus towards front shroud 36; And release side grease chamber 130, when lock-up clutch 120 will be discharged, improve the interior pressure of this release side grease chamber 130, thus lock-up clutch piston 124 is pushed towards the direction left from front shroud 36, by making front shroud 36 and lock-up clutch piston 124 via lock-up clutch friction plate 126 friction apply, between above-mentioned front shroud 36 and lock-up clutch piston 124, carry out moment of torsion transmission.Lock-up clutch 120 carries out moment of torsion transmission via the rubbing surface between lock-up clutch friction plate 126 and front shroud 36.In other words, lock-up clutch 120 via a rubbing surface by front shroud 36 and lock-up clutch piston 124 interconnected.
Above-mentioned engaging side grease chamber 128 is surrounded by lock-up clutch piston 124, front shroud 36 and turbine blade 44 etc. and is formed.In addition, above-mentioned release side grease chamber 130 is surrounded by lock-up clutch piston 124, front shroud 36 and clutch drum 106 etc. and is formed.Lock-up clutch 120 is the veneer clutches with the hydraulic actuator namely leaning on the sidewall portion 36a of motor 14 side to be used as the part forming the parts discharging side grease chamber 130 the engine side wall portion of the front shroud 36 as input side rotary component, is configured at the outer circumferential side that clutch K0 intermittently used by motor.
Above-mentioned second vibration damper 122 is the power transfer path that is folded between the front shroud 36 as the input side rotary component of torque-converters 18 and the turbine 42 as outlet side rotary component and is folded in the vibration damper of the power transfer path between motor MG and automatic transmission 20.Further, when the second vibration damper 122 is to observe from the direction orthogonal with the first axle center C1, the part mode overlapping with the first vibration damper 102 is arranged at the outer circumferential side of the first vibration damper 102.
Above-mentioned release side grease chamber 130 have concurrently the hydraulic chamber of the hydraulic actuator as lock-up clutch 120 function and as making working oil (fluid) in torque-converters 18 and the function of a part supplying release effluent road 132 in the circulation stream circulated between the above-mentioned hydraulic control circuit 114 of working oil, that circulate for working oil when lock-up clutch 120 discharges in this torque-converters 18.
Above-mentioned release effluent road 132 by be formed at respectively automatic transmission 20 input shaft 48 and determine rachis 62 and and inner ring 64a between, and the cylindric gap 132a be communicated with the above-mentioned hydraulic control circuit 114 exporting the working oil of hydraulic pressure as former pressure after carrying out pressure regulation produced using oil pump 24; Be formed between the sidewall portion of inner ring 64a and the lip part 42b of turbine 42, and the annular gap 132b be communicated with above-mentioned annular gap 132a; Along the lip part 42b of the direction through turbine 42 parallel with the first axle center C1 and the through hole 132c be communicated with above-mentioned annular gap 132b; Be formed at this first vibration damper 102 in first vibration damper 102 side of this through hole 132c, annular gap 132d between clutch K0 and lock-up clutch piston 124 intermittently used by motor; Release side grease chamber 130; And engage the formations such as side grease chamber 128.Working oil is supplied towards release side grease chamber 130 successively by above-mentioned cylindric gap 132a, annular gap 132b, through hole 132c and annular gap 132d.Namely, lock-up clutch 120 has release side grease chamber 130, when this lock-up clutch 120 will be made to discharge, supplies working oil towards this release side grease chamber 130, thus make the interior voltage rise of this release side grease chamber 130 high, and this release side grease chamber 130 is made up of the part on release effluent road 132.The cylindric gap 132a on release effluent road 132 is communicated with above-mentioned hydraulic control circuit 114 by being formed at the not shown oil circuit determining rachis 62.In addition, discharge effluent road 132 have to make as the release by lock-up clutch 120 a large amount of working oils torque-converters 18 and supply in this torque-converters 18 in the circulation stream circulated between the above-mentioned hydraulic control circuit 114 of working oil, when carrying out circulation that this circulation time makes fluid circulate towards the side tended in torque-converters 18 from above-mentioned hydraulic control circuit 114 function toward road.
Input shaft 48 in above-mentioned cylindric gap 132a and determining is provided with the sleeve 66 playing function as bearing part or metal bearing between rachis 62.Fig. 4 is the sectional view from the cross section that the direction of arrow is observed of the IV-IV line illustrated along Fig. 3.As shown in Figure 4, at the first cylindric inner peripheral surface 138 of determining rachis 62 opposed with the outer circumferential face of sleeve 66, in the circumferential direction be formed with multiple (being 5 in the present embodiment) first axial groove 140.In addition, at the first cylindric outer circumferential face 142 of the input shaft 48 opposed with the inner peripheral surface of sleeve 66, in the circumferential direction be formed with multiple (being 4 in the present embodiment) second axial groove 144.Above-mentioned first axial groove 140 and the second axial groove 144 play function as the stream of the part forming above-mentioned release effluent road 132.Further, although the actual internal area discharging effluent road 132 because arranging sleeve 66 diminishes, by arranging above-mentioned first axial groove 140 and the second axial groove 144, the actual internal area discharging effluent road 132 can be suppressed to diminish.
Fig. 5 is the sectional view from the cross section that the direction of arrow is observed of the V-V line illustrated along Fig. 3.As shown in Figure 5, in the outer circumferential face of the boss part 42a of turbine 42, on the first C1 direction, axle center with this boss part 42a's and input shaft 48 between the second cylindric outer circumferential face 146 corresponding to spline telescoping part, in the circumferential direction be formed with multiple (being 3 in the present embodiment) the 3rd axial groove 148.In addition, in the inner peripheral surface determining rachis 62, on the first C1 direction, axle center, determine the second cylindric inner peripheral surface 150 corresponding to spline telescoping part between rachis 62 and above-mentioned inner ring 64a (with reference to Fig. 3) with this, in the circumferential direction be formed with multiple (being 4 in the present embodiment) four-axial groove 152.Above-mentioned 3rd axial groove 148 and four-axial groove 152 play function as the stream of the part forming above-mentioned release effluent road 132.And, because of turbine 42 with the spline telescoping part between input shaft 48 and overlapped when determining the observing from the direction orthogonal with the first axle center C1 with the spline telescoping part between inner ring 64a of rachis 62, discharge the actual internal area on effluent road 132 thus to diminish, but by arranging above-mentioned 3rd axial groove 148 and four-axial groove 152 can suppress the actual internal area discharging effluent road 132 to diminish.
As shown in Figure 3, for release effluent road 132 in, be formed at the gap of determining between leaf 46 and turbine blade 44, being positioned at the above-mentioned inner circumferential side of determining leaf 46 and turbine blade 44 and comparing the outer circumferential side of through hole 132c by the annular gap 132b of outer radial periphery side, sealed in liquid-tight manner by sealed member 136.Sealing parts 136 are arranged at the annular protrusions projecting towards the lip part 42b side of turbine 42 from the sidewall portion of inner ring 64a and between the annular protrusions that the sidewall portion side of the inner circumferential side of this annular protrusions from lip part 42b towards inner ring 64a is projecting.
Lock-up clutch 120 carries out engaging release control by above-mentioned hydraulic control circuit 114.In above-mentioned engaging release control, make can the torque capacity of transferring power and the engaging power of lock-up clutch 120 such as changing continuously of lock-up clutch 120 by the pressure regulation of the linear solenoid valve in above-mentioned hydraulic control circuit 114 etc.Under the fastening state of lock-up clutch 120, the front shroud 36 as the input side rotary component of torque-converters 18 is directly linked with the turbine 42 as outlet side rotary component.That is, under the fastening state of lock-up clutch 120, the power from motor 14 inputs to automatic transmission 18 via front shroud 36, second vibration damper 122, turbine blade 44 and turbine 42 successively.On the other hand, under the releasing state of lock-up clutch 120, the power being passed to the front shroud 36 of torque-converters 18 is passed to turbine 42 via fluid.
In addition, torque-converters 18 is provided with the part when lock-up clutch 120 engages for the engaging effluent road 156 of working oil circulation.Above-mentioned engaging effluent road 156 is made up of annular gap 156a and cylindric gap 156b etc., wherein, above-mentioned annular gap 156a is formed between back cover 38 and Ding Ye 46, above-mentioned cylindric gap 156b be formed at tubular pump live axle 58 and overrunning clutch 64 inner ring 64a, determine between rachis 62, and to be communicated with respectively with above-mentioned annular gap 156a and above-mentioned hydraulic control circuit 114.The cylindric gap 156b on engaging effluent road 156 is communicated with above-mentioned hydraulic control circuit 114 by being formed at the not shown oil circuit determining rachis 62.In addition, engage effluent road 156 have make a large amount of working oils in torque-converters 18 as the release by lock-up clutch 120 and supply in this torque-converters 18 in the circulation stream circulated between the above-mentioned hydraulic control circuit 114 of working oil, when the function of carrying out the circulation return road that this circulation time makes fluid circulate towards the side tending to above-mentioned hydraulic control circuit 114 in torque-converters 18.
The power transfer path of power transmission apparatus for vehicle 12 between motor 14 and driving wheel 16 of the present embodiment possesses torque-converters (fluid transmission means) 18, and this torque-converters 18 has: the back cover (input side rotary component) 38 being provided with multiple pump blade 40, be provided with the turbine shaft (outlet side rotary component) 42 accepted from multiple turbine blades 44 of the fluid stream of this pump blade 40, and be provided be disposed between pump blade 40 and turbine blade 44 determine leaf blade 45 determine leaf 46, wherein, power transmission apparatus for vehicle 12 possesses driving axle housing (housing) 22, this driving axle housing 22 has by being arranged at the separated with the spacing wall 68 of motor 14 opposition side of torque-converters 18, first Room R1 of storage torque-converters 18 and be formed at this spacing wall 68 with the second Room R2 of torque-converters 18 opposition side, above-mentioned first Room R1 and the second Room R2 is isolated mutually in liquid-tight manner by oil sealing 70, this oil sealing 70 seals the gap between the inner peripheral surface of the through hole 69 being formed at spacing wall 68 and the outer circumferential face of tubular pump live axle 58 in liquid-tight manner, leaning on the sidewall portion of spacing wall 68 side and determining to be equipped with the first thrust-bearing 94 between leaf 46 at back cover 38, when this first thrust-bearing 94 is arranged to observe from the direction orthogonal with the first axle center C1, a part is overlapping with oil sealing 70.So, with the first thrust-bearing 94 above-mentioned when observing from the direction orthogonal with the first axle center C1 not compared with the situation of oil sealing 70 overlap, can by this first thrust-bearing 94, configure near spacing wall 68 side with the adjacent parts such as overrunning clutch 64 arranged of this first thrust-bearing 94, therefore, it is possible to shorten the distance between the outer cover entirety of the torque-converters 18 of above-mentioned first thrust-bearing 94 of storage and overrunning clutch 64 and spacing wall 68.Therefore, it is possible to shorten the entire axial length of power transmitting deice 12.
In addition, according to the power transmission apparatus for vehicle 12 of the present embodiment, back cover (input side rotary component) 38 has cyclic lug 38a, this cyclic lug 38a is formed by back cover 38 leaning on a part in the sidewall portion of spacing wall 68 side, corresponding with the first thrust-bearing 94 radial position to give prominence to towards spacing wall 68 side throughout complete cycle, and the first thrust-bearing 94 is configured in this cyclic lug 38a.So, can by above-mentioned first thrust-bearing 94, configure near spacing wall 68 side with the adjacent parts such as overrunning clutch 64 arranged of this first thrust-bearing 94.
In addition, according to the power transmission apparatus for vehicle 12 of the present embodiment, torque-converters 18 possesses motor and intermittently uses clutch K0, and this motor intermittently optionally links the bent axle 99 of motor 14 and the front shroud (input side rotary component) 36 of this torque-converters 18 with clutch K0.According to the present embodiment, the first thrust-bearing 94, overrunning clutch 64 configure near spacing wall 68 side, thereby, it is possible to above-mentioned motor to be intermittently configured in compactly the space vacated in the outer cover of torque-converters with clutch K0.
In addition, power transmission apparatus for vehicle 12 according to the present embodiment possesses motor MG, this motor MG is configured on the second axle center C2 parallel with above-mentioned first axle center C1, and link via tubular pump live axle (cylindric running shaft) 58 and with the motor link rotary component 84 that this tubular pump live axle 58 links with back cover (input side rotary component) 38 respectively, spacing wall 68 has support 68b, this support 68b is given prominence to towards the second R2 side, Room throughout complete cycle by a part for the radial position of spacing wall 68 and is formed, motor link rotary component 84 supports as rotating via the support 68b of the second bearing 90 by spacing wall 68, cyclic lug 38a is positioned at the inner circumferential side of the support 68b of spacing wall 68.So, such as, assist by utilizing the output of above-mentioned motor MG to this motor 14 when making vehicle travel by motor 14 or motor 14 stopped and utilizing above-mentioned motor MG to drive vehicle etc., the fuel availability of vehicle can be improved.In addition, even if when arranging motor link rotary component 84 respectively in order to the back cover 38 of motor MG and torque-converters 18 is linked and be used for this motor link rotary component 84 to support the support 68b of the spacing wall 68 for rotating, also above-mentioned first thrust-bearing 94, overrunning clutch 64 can be configured near spacing wall 68 side.
In addition, according to the power transmission apparatus for vehicle 12 of the present embodiment, possesses automatic transmission (driving mechanism) 20, this automatic transmission 20 is configured in and motor 14 opposition side relative to torque-converters 18 on the first C1 direction, axle center, and the power from this torque-converters 18 is transmitted towards driving wheel 16, the turbine 42 of torque-converters 18 is linking by the position of automatic transmission 20 side and the input shaft 48 of this automatic transmission 20 relative to pump blade 40 on the first C1 direction, axle center, determine leaf 46 via overrunning clutch 64 with determine rachis 62 and link in the mode that can not relatively rotate, the inner ring 64a of overrunning clutch 64 with determine linking portion that rachis 62 links and turbine 42 boss part 42a be arranged to observe from the direction orthogonal with the first axle center C1 with the linking portion that input shaft 48 links time part or all is overlapping with the first thrust-bearing 94 and oil sealing 70 respectively.So, the linking portion linked with input shaft 48 of the boss part 42a of turbine 42 and the inner ring 64a of overrunning clutch 64 with determine the linking portion that rachis 62 links and be arranged on outside the outer cover of torque-converters 18 on the first C1 direction, axle center.Therefore, compared with being arranged at the situation in above-mentioned outer cover with above-mentioned each linking portion, the length on the first C1 direction, axle center of this outer cover can be shortened, therefore, it is possible to shorten the entire axial length of power transmitting deice 12.
Above, with reference to accompanying drawing, one embodiment of the invention have been described in detail, but the present invention is not limited to this embodiment, also can be implemented in other way and obtain.
Such as, in the above-described embodiment, torque-converters 18 possesses the motor MG be configured on the second axle center C2 parallel with the first axle center C1 of this torque-converters 18, but is not to possess above-mentioned motor MG.In addition, even if when torque-converters 18 possesses above-mentioned motor MG, be not above-mentioned motor MG must be configured on the second axle center C2 parallel with the first axle center C1 yet.Also motor MG can be configured on the first axle center C1.
In addition, in the above-described embodiment, torque-converters 18 possesses motor and intermittently uses clutch K0 and lock-up clutch 120, but is not must possess above-mentioned motor intermittently to use clutch K0 and lock-up clutch 120.
In addition, in the above-described embodiment, power transmission apparatus for vehicle 12 possesses automatic transmission 20 at the back segment of torque-converters 18, but be not to possess above-mentioned automatic transmission 20, there is the input shaft linked with the turbine 42 of torque-converters 18 and the driving mechanism transmitted towards back segment by the power inputing to this input shaft as long as possess.
In addition, in the above-described embodiment, motor MG via the Transmitted chains 88 be wrapping with in the ring-type of the first motor link gear 82 and the second motor link gear 86 and the back cover 38 as the input side rotary component of torque-converters 18 active link, but also can not via above-mentioned Transmitted chains 88 via such as gear equity and back cover 38 active link.
In addition, in the above-described embodiment, the input shaft 48 of automatic transmission 20 is determined rachis 62 in the inner circumferential side of determining rachis 62 and is supported as rotating by this via sleeve 66, but be not limited to above-mentioned sleeve 66, such as, also can be supported by other the bearing part such as needle roller bearing (needle bearing).
In addition, in the above-described embodiment, determine rachis 62 and be arranged at pump cover 50 integratedly, thus non rotating under normal conditions, but be not must non rotating under normal conditions.Such as, determine rachis 62 can be configured to link with the output shaft of motor and rotate by this motor thus the capacity coefficient of torque-converters 18 can be made to change, or, also can be configured to link via break and pump cover 50, optionally switch to rotation status and non-rotating state by utilizing this break and the capacity coefficient of torque-converters 18 can be made to change.
In addition, in the above-described embodiment, power transmission apparatus for vehicle 8 is horizontally placed on FF(front-mounted engine/front-wheel drive together with motor 14) front of the vehicle 6 of type, but be not limited thereto, such as also can at FR(front-mounted engine/rear wheel drive) type vehicle or RR(rear engine/rear wheel drive) type vehicle etc. other drive in the vehicle of patterns longitudinal or horizontal.
In addition, above-mentioned mode of execution is a mode of execution only, though do not illustrate other mode of execution one by one, the present invention can to carry out various change based on the knowledge of those skilled in the art in the scope not departing from its purport, improvement and the mode obtained implemented.
Description of reference numerals:
12: power transmission apparatus for vehicle; 14: motor; 16: driving wheel; 18: torque-converters; 20: automatic transmission (driving mechanism); 22: driving axle housing (housing); 38: back cover (input side rotary component); 38a: cyclic lug; 40: pump blade; 42: turbine (outlet side rotary component); 44: turbine blade; 45: determine leaf blade; 46: determine leaf; 48: input shaft; 58: tubular pump live axle (cylindric running shaft); 62: determine rachis; 64: overrunning clutch; 64a: inner ring; 68: spacing wall; 68b: support; 70: oil sealing; 84: motor link rotary component; 90: the second bearings (bearing); 96: the second thrust-bearings (thrust-bearing); 99: bent axle; K0: motor intermittently uses clutch; MG: motor; R1: the first Room; R2: the second Room; C1: the first axle center (axle center of torque-converters); C2: the second axle center (the second axle center).

Claims (4)

1. a power transmission apparatus for vehicle,
The power transfer path of described power transmission apparatus for vehicle between motor and driving wheel possesses torque-converters, and described torque-converters has: the input side rotary component being provided with multiple pump blade; Be provided with the outlet side rotary component accepted from multiple turbine blades of the fluid stream of described pump blade; And be provided be disposed between described pump blade and described turbine blade determine leaf blade determine leaf,
The feature of described power transmission apparatus for vehicle is,
Described power transmission apparatus for vehicle possesses housing, described housing have by be arranged at described torque-converters, first Room of receiving described torque-converters separated with the spacing wall of described motor opposition side and be formed at described spacing wall with the second Room of described torque-converters opposition side
Described first Room and described second Room are isolated mutually in liquid-tight manner by oil sealing, described oil sealing seal in liquid-tight manner described spacing wall inner peripheral surface and from described input side rotary component towards the gap between the outer circumferential face of the projecting cylindric running shaft in described second side, Room
In the sidewall portion by described spacing wall side of described input side rotary component and describedly determine to be equipped with thrust-bearing between leaf,
When described thrust-bearing is arranged to observe from the direction orthogonal with the axle center of described torque-converters, part or all is overlapping with described oil sealing,
Determine leaf and support between the described on-rotatably moving part determining leaf to be provided with overrunning clutch described, a part for described overrunning clutch is compared the described inner ring determining leaf and described overrunning clutch and is given prominence to towards described second side, Room,
Described input side rotary component has cyclic lug, described cyclic lug is formed by described input side rotary component leaning on a part in the sidewall portion of described spacing wall side, corresponding with described thrust-bearing radial position to give prominence to towards described spacing wall side throughout complete cycle
A part for described thrust-bearing, described overrunning clutch is accommodated in described cyclic lug.
2. power transmission apparatus for vehicle according to claim 1, is characterized in that,
Described torque-converters possesses motor and intermittently uses clutch, described motor intermittently optionally links the bent axle of described motor and the input side rotary component of described torque-converters with clutch, and described motor to be intermittently incorporated in described input side rotary component by the described engine side that clutch is in described outlet side rotary component and from part or all state overlapping with described oil sealing and described thrust-bearing when observing with the direction of described axis parallel.
3. power transmission apparatus for vehicle according to claim 1 and 2, is characterized in that,
Described power transmission apparatus for vehicle possesses motor, described motor is configured on the second axle center with described axis parallel, and respectively via described cylindric running shaft and be linked to the motor link rotary component of described cylindric running shaft and described input side rotary component links
Described spacing wall has support, and described support is given prominence to towards described second side, Room throughout complete cycle by a part for the radial position of described spacing wall and formed,
Described motor link rotary component supports as rotating via the support of bearing by described spacing wall,
Described cyclic lug is positioned at the inner circumferential side of the support of described spacing wall.
4. power transmission apparatus for vehicle according to claim 1 and 2, is characterized in that,
Described power transmission apparatus for vehicle possesses driving mechanism, and described driving mechanism is configured in described motor opposition side relative to described torque-converters on described axis direction, and is transmitted towards described driving wheel by the power from described torque-converters,
Described outlet side rotary component is linking by the position of described driving mechanism side and the input shaft of described driving mechanism relative to described pump blade on described axis direction,
Described determine leaf via overrunning clutch with determine rachis and link in the mode that can not relatively rotate,
The inner ring of described overrunning clutch with described determine linking portion that rachis links and described outlet side rotary component be arranged to observe from the direction orthogonal with described axle center with the linking portion that described input shaft links time part or all is overlapping with described thrust-bearing and described oil sealing respectively.
CN201080070340.1A 2010-11-24 2010-11-24 Vehicular power transmission device Expired - Fee Related CN103228954B (en)

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US20140256506A1 (en) 2014-09-11
US8974339B2 (en) 2015-03-10

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